US12473951B2 - Clutch device and motorcycle - Google Patents

Clutch device and motorcycle

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Publication number
US12473951B2
US12473951B2 US18/700,071 US202218700071A US12473951B2 US 12473951 B2 US12473951 B2 US 12473951B2 US 202218700071 A US202218700071 A US 202218700071A US 12473951 B2 US12473951 B2 US 12473951B2
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United States
Prior art keywords
presser
center
clutch
plate
cam surface
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Active
Application number
US18/700,071
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English (en)
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US20250237274A1 (en
Inventor
Yuki AONO
Junichi Nishikawa
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FCC Co Ltd
Original Assignee
FCC Co Ltd
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Publication of US20250237274A1 publication Critical patent/US20250237274A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/22—Friction clutches with axially-movable clutching members
    • F16D13/38—Friction clutches with axially-movable clutching members with flat clutching surfaces, e.g. discs
    • F16D13/52—Clutches with multiple lamellae ; Clutches in which three or more axially moveable members are fixed alternately to the shafts to be coupled and are pressed from one side towards an axially-located member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D13/00—Friction clutches
    • F16D13/58—Details
    • F16D13/74—Features relating to lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/12—Mechanical clutch-actuating mechanisms arranged outside the clutch as such
    • F16D2023/123—Clutch actuation by cams, ramps or ball-screw mechanisms

Definitions

  • the present invention relates to a clutch device allowing or blocking transfer of a rotation driving force of a drive shaft, rotationally drivable by a prime mover, to a driven shaft driving a driven body, and a motorcycle including the same.
  • a vehicle such as a two-wheeled vehicle (motorcycle), a four-wheeled vehicle or the like includes a clutch device located between a prime mover such as an engine or the like and a driven body such as a wheel or the like to allow or block transfer of a rotation driving force of the prime mover to the driven body.
  • a clutch device a plurality of input-side rotating plates rotatable by a rotation driving force of the prime mover and a plurality of output-side rotating plates coupled with the driven body are opposed to each other, and are put into close contact with, or are separated from, each other.
  • the clutch device may optionally allow or block transfer of the rotation driving force.
  • Japanese Patent Application Publication No. 2010-151232 discloses a clutch device including a center clutch coupled with a driven body via a shaft to hold the output-side rotating plates and a pressure clutch pressing the output-side rotating plates held by the center clutch, the pressure clutch being fitted to an inner circumferential portion of a center-side fitting portion of the center clutch to be slidable relative to the center clutch in an axial direction.
  • the center-side fitting portion is formed in the vicinity of the inner circumferential portion of the output-side rotating plates and the input-side rotating plates, which are at a diametrically outer position of the clutch device in consideration of the ease of spreading clutch oil, flowing out of a tip of the shaft, in the clutch device.
  • the clutch device described in Japanese Patent Application Publication No. 2010-151232 has a problem that the center-side fitting portion is formed at the diametrically outer position in the clutch device, and therefore, the slidable portion needs to have a long diameter and thus has a large sliding resistance, which makes it difficult to decrease the size of the clutch device.
  • Example embodiments of the present invention provide clutch devices that are decreased in size and motorcycles including the same.
  • a clutch device for allowing or blocking transfer of a rotation driving force of a drive shaft to a driven shaft includes a clutch center including a plate holder holding an output-side rotating plate facing an input-side rotating plate rotationally drivable by rotational driving of the drive shaft, the clutch center being rotationally drivable together with the driven shaft, a plate presser facing the clutch center and displaceable toward or away from the clutch center and rotatable with respect to the clutch center to press the input-side rotating plate or the output-side rotating plate, and a center cylindrical portion, wherein the clutch center includes a driven shaft coupling portion coupled with a tip portion of the driven shaft, and the center cylindrical portion includes a center fitting portion slidably fitted to the driven shaft coupling portion and a cylindrical oil receiver adjacent to the center fitting portion to receive clutch oil flowing out of a flow-out portion of the driven shaft.
  • the center fitting portion of the center cylindrical portion of the plate presser is slidably fitted to the outer surface of the driven shaft coupling portion of the clutch center, and the oil receiver of the center cylindrical portion receives the clutch oil flowing out of the flow-out portion of the driven shaft.
  • the clutch oil flowing out of the driven shaft may be effectively guided to a sliding portion along which the clutch center and the plate presser slide against each other and then caused to flow to the outside of the sliding portion (outside of the center cylindrical portion).
  • the clutch oil may lubricate the inside of the clutch device.
  • the sliding portion of the clutch center and the plate presser may be provided at the driven shaft coupling portion, which is close to a central portion of the clutch center.
  • the clutch device may make the sliding portion small, and thus may be decreased in size.
  • the oil receiver includes a slope at least at a portion of an inner circumferential surface thereof, the slope expanding diametrically outward toward the center fitting portion.
  • the clutch oil flowing out of the driven shaft may be effectively guided toward the center fitting portion. Therefore, the clutch oil may be guided to the sliding portion of the clutch center and the plate presser more effectively and then caused to flow to the outside of the sliding portion (outside of the center cylindrical portion). Thus, the clutch oil may lubricate the inside of the clutch device.
  • the center cylindrical portion includes an oil path expansion portion in a circumferential direction in which the center fitting portion is provided, the oil path expansion portion expanding diametrically outward and defining a gap between the oil path expansion portion and an outer circumferential portion of the driven shaft coupling portion.
  • the clutch device includes the oil path expansion portion in a portion of the center cylindrical portion in a circumferential direction in which the center fitting portion is provided.
  • the oil path expansion portion expands diametrically outward and defines a gap between the oil path expansion portion and the outer circumferential portion of the driven shaft coupling portion. Therefore, the clutch oil in the center cylindrical portion may be effectively guided to the outside of the center cylindrical portion via the oil path expansion portion.
  • the gap between the oil path expansion portion and the driven shaft coupling portion by the oil path expansion portion is larger than the gap between the driven shaft coupling portion and the center fitting portion.
  • the oil path expansion portion extends from the center fitting portion to the oil receiver.
  • the oil path expansion portion reaches the oil receiver, or extends to enter the oil receiver, from the center fitting portion. Therefore, the clutch oil in the center cylindrical portion may be effectively guided to the outside of the center cylindrical portion via the oil path expansion portion.
  • the center cylindrical portion includes an opening in a portion thereof in a circumferential direction in which the center fitting portion is provided, the opening being defined by a cut-off portion.
  • the opening is at a position facing the central portion of the plate holder in the axial direction thereof. Therefore, the clutch oil in the center cylindrical portion may be effectively guided to the outside of the center cylindrical portion, more specifically, to the central portion of the plate holder in the axial direction thereof, via the opening. That is, the clutch device may supply the clutch oil in the center cylindrical portion to the central portion, where the input-side rotating plate and the output-side rotating plate are aligned, and thus may effectively supply the clutch oil to the entirety of the input-side rotating plate and the output-side rotating plate.
  • the central portion of the plate holder in the axial direction, at which the opening is provided is not necessarily the central portion in a strict sense, but includes the central portion and the vicinity thereof.
  • the opening extends from the center fitting portion to the oil receiver.
  • the opening reaches the oil receiver, or extends to enter the oil receiver, from the center fitting portion. Therefore, the clutch oil in the center cylindrical portion may be effectively guided to the outside of the center cylindrical portion via the opening.
  • Example embodiments of the present invention provide clutch devices each capable of supplying a larger amount of clutch oil to the input-side rotating plate and the output-side rotating plate.
  • a clutch device for allowing or blocking transfer of a rotation driving force of a drive shaft to a driven shaft includes a clutch center including a plate holder holding an output-side rotating plate facing an input-side rotating plate rotationally drivable by rotational driving of the drive shaft, the clutch center being rotationally drivable together with the driven shaft, a plate presser facing the clutch center and displaceable toward or away from the clutch center and rotatable with respect to the clutch center to press the input-side rotating plate or the output-side rotating plate, and a center cylindrical portion, wherein the clutch center includes a driven shaft coupling portion coupled with a tip portion of the driven shaft, and the center cylindrical portion includes a center fitting portion slidably fitted to the driven shaft coupling portion and a recessed portion provided in a portion of the plate presser in a circumferential direction in which the center fitting portion is provided, the recessed portion expanding diametrically outward and defining a gap between the recessed portion and an outer circumferential portion of
  • the clutch oil flowing out of the flow-out portion of the driven shaft flows in the recessed portion.
  • the recessed portion defines a gap between the recessed portion and the outer circumferential portion of the driven shaft coupling portion. Therefore, the clutch oil flowing in the recessed portion flows to the outside of the center cylindrical portion more effectively, and thus a larger amount of the clutch oil may be supplied to the input-side rotating plate and the output-side rotating plate.
  • the recessed portion is located between two of the presser-side cam portions adjacent to each other in the circumferential direction.
  • the recessed portion is located closer to the presser-side assist cam surface.
  • the recessed portion is located closer to the presser-side assist cam surface.
  • the clutch oil flowing to the outside of the center cylindrical portion is effectively supplied also to the presser-side assist cam surface, and therefore, may alleviate abrasion of the presser-side assist cam surface and the center-side assist cam surface.
  • the recessed portion is located closer to the presser-side slipper cam surface.
  • the recessed portion is located closer to the presser-side slipper cam surface.
  • the stress applied to the presser-side slipper cam surface is smaller than the stress applied to the presser-side assist cam surface. Therefore, the recessed portion is provided closer to the presser-side slipper cam surface, so that the clutch oil may be caused to flow to the outside of the center cylindrical portion while the strength of the center cylindrical portion is kept sufficiently high.
  • the recessed portion is provided in an entirety of a region of the center cylindrical portion extending from at least a central portion in an axial direction thereof to an end thereof on a side of the clutch center.
  • the clutch oil flowing out of the flow-out portion of the driven shaft may be caused to flow to the outside of the center cylindrical portion more certainly, and thus a larger amount of the clutch oil may be supplied to the input-side rotating plate and the output-side rotating plate.
  • the recessed portion is provided in the center cylindrical portion so as to expand diametrically outward.
  • the recessed portion of the plate presser is provided in the center cylindrical portion so as to expand diametrically outward.
  • the clutch oil flowing in the recessed portion flows to the outside of the center cylindrical portion more effectively, and thus a larger amount of the clutch oil may be supplied to the input-side rotating plate and the output-side rotating plate.
  • the recessed portion is located closer to the presser-side assist cam surface than to the presser-side cam surface.
  • the recessed portion is located closer to the presser-side assist cam surface than to the presser-side cam surface.
  • the recessed portion is located closer to the presser-side slipper cam surface than to the presser-side assist cam surface.
  • the recessed portion is located closer to the presser-side slipper cam surface than to the presser-side assist cam surface.
  • the stress applied to the presser-side slipper cam surface is smaller than the stress applied to the presser-side assist cam surface. Therefore, the recessed portion is provided closer to the presser-side slipper cam surface, so that the clutch oil may be caused to flow to the outside of the center cylindrical portion while the strength of the center cylindrical portion is kept sufficiently high.
  • the recessed portion is provided in an entirety of a region of the center cylindrical portion extending from at least a central portion in an axial direction thereof to an end thereof on the side of the clutch center.
  • the clutch oil flowing out of the flow-out portion of the driven shaft may be caused to flow to the outside of the center cylindrical portion more certainly, and thus a larger amount of the clutch oil may be supplied to the input-side rotating plate and the output-side rotating plate.
  • the center cylindrical portion includes an opening defined by a cut-off portion in the circumferential direction.
  • the clutch oil in the center cylindrical portion may be effectively guided to the outside of the center cylindrical portion via the opening.
  • the clutch center includes a plurality of center-side cam portions located diametrically outward of the driven shaft coupling portion, the plurality of center-side cam portions each including a center-side assist cam surface to generate a force applicable in a direction to cause the plate presser to approach the clutch center, in order to increase a pressing force between the input-side rotating plate and the output-side rotating plate, when the clutch center rotates with respect to the plate presser, and also including a center-side slipper cam surface to separate the plate presser from the clutch center, in order to decrease the pressing force between the input-side rotating plate and the output-side rotating plate, when the clutch center rotates with respect to the plate presser
  • the plate presser includes a plurality of presser-side cam portions located diametrically outward of the center cylindrical portion, the plurality of presser-side cam portions each including a presser-side assist cam surface contactable with the center-side assist cam surface and generating a force in such a direction as to cause the plate presser to
  • the opening is located between two of the presser-side cam portions adjacent to each other in the circumferential direction.
  • the opening is located closer to the presser-side assist cam surface.
  • the clutch oil flowing to the outside of the center cylindrical portion is effectively supplied also to the presser-side assist cam surface, and therefore, may alleviate abrasion of the presser-side assist cam surface and the center-side assist cam surface.
  • the opening is located closer to the presser-side slipper cam surface.
  • the opening is located closer to the presser-side slipper cam surface.
  • the stress applied to the presser-side slipper cam surface is smaller than the stress applied to the presser-side assist cam surface. Therefore, the recessed portion is provided closer to the presser-side slipper cam surface, so that the clutch oil may be caused to flow to the outside of the center cylindrical portion while the strength of the center cylindrical portion is kept sufficiently high.
  • the opening extends from an end of the presser-side assist cam surface on the side of the first circumferential direction to an end of the presser-side slipper cam surface on the side of the second circumferential direction.
  • a larger amount of the clutch oil flows to the outside via the opening. Therefore, a larger amount of the clutch oil may be supplied to the input-side rotating plate and the output-side rotating plate.
  • a direction in which the plate presser approaches the clutch center is a first direction and a direction in which the plate presser moves away from the clutch center is a second direction
  • an end of the opening on the side of the second direction is located ahead, in the second direction, of an end of the presser-side slipper cam surface on the side of the second direction.
  • the opening includes the first portion having the first length in the circumferential direction and the second portion having the second length in the circumferential direction.
  • a motorcycle includes a clutch device according to one of the example embodiments of the present invention described herein.
  • FIG. 1 is a cross-sectional view generally showing an overall configuration in a clutch-ON state of a clutch device according to an example embodiment of the present invention.
  • FIG. 3 is a perspective view showing a configuration on the side of the center fitting portion of the plate presser according to a modification of an example embodiment of the present invention.
  • FIG. 4 is a perspective view showing a configuration on the side of the center fitting portion of the plate presser according to another modification of an example embodiment of the present invention.
  • FIG. 5 is a perspective view showing a configuration on the side of the center fitting portion of the plate presser according to still another modification of an example embodiment of the present invention.
  • FIG. 6 is a perspective view showing a configuration on the side of the center fitting portion of the plate presser according to still another modification of an example embodiment of the present invention.
  • FIG. 7 is a perspective view showing a configuration of a clutch center shown in FIG. 1 .
  • FIG. 8 is a plan view showing a configuration on the side of the center fitting portion of the plate presser shown in FIG. 1 .
  • FIG. 9 is a side view showing a configuration of the plate presser shown in FIG. 1
  • FIG. 11 is a side view showing a configuration of the plate presser according to still another modification of an example embodiment of the present invention.
  • FIG. 12 is a side view showing a configuration of the plate presser according to still another modification of an example embodiment of the present invention.
  • FIG. 13 is a side view showing a configuration of the plate presser according to still another modification of an example embodiment of the present invention.
  • FIG. 1 is a cross-sectional view generally showing an overall configuration of a clutch device 100 according to an example embodiment of the present invention.
  • the clutch device 100 is a mechanical device allowing or blocking transfer of a driving force of an engine (not shown), which is a prime mover of a motorcycle (motorbike), to a wheel (not shown), which is a driven body, and is located between the engine and a transmission (not shown).
  • the clutch device 100 includes a clutch outer 101 .
  • the clutch outer 101 is a component holding input-side rotating plates 105 and transferring a driving force of the engine to the input-side rotating plates 105 , and is formed of an aluminum alloy material molded into a bottomed cylindrical shape. More specifically, a cylindrical portion of the clutch outer 101 includes a rotating plate holder 101 a formed therein, and the rotating plate holder 101 a includes an internal gear-shaped spline.
  • a plurality of (five in this example embodiment) input-side rotating plates 105 are spline-fitted to, and thus held by, the rotating plate holder 101 a in a state where the input-side rotating plates 105 are displaceable in an axial direction of the clutch outer 101 and are rotatable integrally with the clutch outer 101 .
  • the clutch outer 101 includes a coupling hole 101 b in a central portion of a left side surface (in the figure) thereof.
  • a boss 103 a of an input rotating body 103 described below is attached to the coupling hole 101 b in a state where the boss 103 a is slidably fitted to the coupling hole 101 b .
  • the input rotating body 103 is attached to the clutch outer 101 via a rivet 102 a , a side plate 102 b , a torque damper 102 c and a separation spring 102 d.
  • the input rotating body 103 is a metal gear component rotationally drivable in a state of meshing with a driving gear coupled with a drive shaft (not shown) such as, for example, a crank shaft that rotates by being driven by the prime mover such as the engine or the like.
  • a drive shaft such as, for example, a crank shaft that rotates by being driven by the prime mover such as the engine or the like.
  • the boss 103 a formed in the central portion of the input rotating body 103 is rotatably supported by a shaft 120 via a needle bearing 104 . That is, the clutch outer 101 is rotationally drivable integrally with the input rotating body 103 concentrically with the shaft 120 but independently from the shaft 120 .
  • the shaft 120 is an example of a driven shaft.
  • the input-side rotating plates 105 are flat ring-shaped components that are pressed onto the output-side rotating plates 106 , and are formed of a thin aluminum plate molded into a ring shape.
  • an external gear meshing with the internal gear-shaped spline of the clutch outer 101 is formed at an outer circumferential portion of each of the input-side rotating plates 105 .
  • Both of side surfaces (front and rear surfaces) of each of the input-side rotating plates 105 each have friction members (not shown), formed of a plurality of paper sheets, attached thereon, and oil grooves (not shown) are formed between the friction members.
  • the output-side rotating plates 106 are flat ring-shaped components that are pressed onto the input-side rotating plates 105 described above, and are formed of a thin SPCC (steel plate cold commercial) plate punched into a ring shape.
  • the output-side rotating plates 106 (five plates in this example embodiment) are held by a clutch center 110 and a plate presser 111 in a state of being located alternately with the plurality of input-side rotating plates 105 inside the clutch outer 101 .
  • An internal gear-shaped spline is formed at an inner circumferential portion of each of the output-side rotating plates 106 .
  • the internal gear-shaped spline is spline-fitted to a plate holder 110 e formed in the clutch center 110 and also to a plate sub holder 111 e formed in the plate presser 111 .
  • the friction members, which are provided on each of the input-side rotating plates 105 may be provided on each of the output-side rotating plates 106 instead of on each of the input-side rotating plates 105 .
  • the clutch center 110 is a component housing the input-side rotating plates 105 and also the output-side rotating plates 106 and transferring the driving force of the engine toward the transmission, and is formed of an aluminum alloy material molded into a generally cylindrical shape. More specifically, the clutch center 110 mainly includes a driven shaft coupling portion 110 a , a ring-shaped intermediate portion 110 b and the plate holder 110 e integrally formed together.
  • the driven shaft coupling portion 110 a is a portion fitted to an inner surface of the plate presser 111 and coupled with the shaft 120 , and extends in an axial direction of the clutch center 110 in a central portion of the clutch center 110 .
  • the driven shaft coupling portion 110 a is formed to be cylindrical.
  • An outer circumferential surface of the driven shaft coupling portion 110 a is formed to be a smooth cylindrical surface on which a center fitting portion 112 a of the plate presser 111 is slidable in the axial direction and a circumferential direction of the clutch center 110 .
  • An inner circumferential surface of the driven shaft coupling portion 110 a includes an internal gear-shaped spline formed in the axial direction thereof, and the shaft 120 is spline-fitted to the spline. That is, the clutch center 110 is rotatable integrally with the shaft 120 concentrically with the clutch outer 101 and the shaft 120 .
  • the ring-shaped intermediate portion 110 b is a flange-shaped portion formed between the driven shaft coupling portion 110 a and the plate holder 111 e .
  • Three cylindrical supports 110 c are formed on the ring-shaped intermediate portion 110 b , along the circumferential direction.
  • the three cylindrical supports 110 c are cylindrical portions each extending like a column in the axial direction of the clutch center 110 to support the plate presser 111 .
  • the cylindrical supports 110 c each have a female screw formed in an inner circumferential portion thereof. These three cylindrical supports 110 c are formed at an equal interval along the circumferential direction of the clutch center 110 .
  • the ring-shaped intermediate portion 110 b includes a plurality of trapezoidal center-side cam portions 110 d formed therein.
  • the center-side cam portions 110 d each have a cam surface formed of a slope acting as an Assist & Slipper (registered trademark) mechanism.
  • the Assist & Slipper mechanism generates an assist torque as a force increasing a contact pressure force between the input-side rotating plates 105 and the output-side rotating plates 106 or a slipper torque as a force to separate the input-side rotating plates 105 and the output-side rotating plates 106 from each other on an early stage and shifting these plates into a half-clutch state.
  • the clutch center 110 includes three center-side cam portions 110 d .
  • the number of the center-side cam portions 110 d is not limited to three.
  • the Assist & Slipper (registered trademark) mechanism may be omitted to form the ring-shaped intermediate portion 110 b.
  • the center-side cam portions 110 d are located diametrically outward of the driven shaft coupling portion 110 a .
  • the center-side cam portions 110 d are located in the circumferential direction of the clutch center 110 at an equal interval.
  • the center-side cam portions 110 d each have a center-side assist cam surface 110 da and a center-side slipper cam surface 110 ds .
  • the center-side assist cam surface 110 da is configured to generate a force in such a direction as to cause the plate presser 111 to approach the clutch center 110 , in order to increase a pressing force (contact pressure force) between the input-side rotating plates 105 and the output-side rotating plates 106 , when the clutch center 110 rotates with respect to the plate presser 111 .
  • the position of the plate presser 111 with respect to the clutch center 110 does not change, and the plate presser 111 does not need to approach the clutch center 110 physically.
  • the plate presser 111 may be physically displaced with respect to the clutch center 110 .
  • a direction in which the plate presser 111 approaches the clutch center 110 will be referred to as a first direction D 1 (see FIG. 9 ).
  • the center-side slipper cam surface 110 ds is configured to separate the plate presser 111 from the clutch center 110 , in order to decrease the pressing force (contact pressure force) between the input-side rotating plates 105 and the output-side rotating plates 106 , when the clutch center 110 rotates with respect to the plate presser 111 .
  • a direction in which the plate presser 111 moves away from the clutch center 110 will be referred to as a second direction D 2 (see FIG. 9 ).
  • the center-side assist cam surface 110 da of one center-side cam portion 110 d and the center-side slipper cam surface 110 ds of the other center-side cam portion 110 d are opposed to each other in the circumferential direction.
  • the plate holder 110 e is a portion holding a portion of the plurality of output-side rotating plates 106 together with the input-side rotating plates 105 , and extends in the axial direction of the clutch center 110 in an outer edge of the clutch center 110 .
  • the plate holder 110 e is cylindrical.
  • the plate holder 110 e includes an outer circumferential portion formed of an external gear-shaped spline, and holds the output-side rotating plates 106 and the input-side rotating plates 105 located alternately in a state where the output-side rotating plates 106 and the input-side rotating plates 105 are displaceable in the axial direction of the clutch center 110 and are rotatable integrally with the clutch center 110 .
  • the plate holder 110 e includes a plate receiver 110 f formed in a left tip portion (in the figure) thereof.
  • the plate receiver 110 f is a portion receiving the output-side rotating plates 106 and the input-side rotating plates 105 pressed by the plate presser 111 and sandwiching the output-side rotating plates 106 and the input-side rotating plates 105 together with the plate presser 111 .
  • the plate receiver 110 f includes a tip portion of the cylindrical plate holder 110 e protruding like a flange diametrically outward.
  • the plate presser 111 is a component pressing the input-side rotating plates 105 to put the input-side rotating plates 105 and the output-side rotating plates 106 into close contact with each other, and is formed of an aluminum alloy material molded into a generally discus shape having an outer diameter substantially the same as an outer diameter of the output-side rotating plates 106 . More specifically, as shown in FIG. 2 , the plate presser 111 mainly includes a center cylindrical portion 111 a , a ring-shaped intermediate portion 111 b and the plate sub holder 111 e integrally formed together.
  • the center cylindrical portion 111 a is a portion that is slidably fitted to an outer surface of the driven shaft coupling portion 110 a and receives a pressing force from a push rod 124 included in the shaft 120 , and is cylindrical.
  • the center cylindrical portion 111 a houses a tip portion 121 of the shaft 120 .
  • the center cylindrical portion 111 a includes the center fitting portion 112 a and an oil receiver 112 b formed therein.
  • the center fitting portion 112 a is a portion fitted to the outer surface of the driven shaft coupling portion 110 a of the clutch center 110 so as to be slidable an axial direction and a circumferential direction of the driven shaft coupling portion 110 a , and is formed to have a cylindrical shape having a constant inner diameter.
  • the inner diameter of the center fitting portion 112 a has a meshing tolerance with which the clutch oil flowing out of the tip portion of the shaft 120 is allowed to be distributed through a region between the center fitting portion 112 a and the driven shaft coupling portion 110 a .
  • the inner diameter of the center fitting portion 112 a is larger by about 0.1 mm, for example, than an outer diameter of the driven shaft coupling portion 110 a .
  • the size tolerance between the inner diameter of the center fitting portion 112 a and the outer diameter of the driven shaft coupling portion 110 a is set appropriately in accordance with the amount of the clutch oil to be distributed.
  • the size tolerance is preferably about 0.1 mm or longer and about 0.5 mm or shorter, for example.
  • the oil receiver 112 b is a portion receiving the pressing force from the push rod 124 included in the shaft 120 and also receiving the clutch oil flowing out of the tip portion of the shaft 120 , and is formed to have a cylindrical shape having an inner diameter shorter than that of the center fitting portion 112 a .
  • a release bearing 112 c is fitted to a right end portion (in the figure) of the oil receiver 112 b , and a slope 112 d is formed between the portion to which the release bearing 112 c is fitted and the center fitting portion 112 a.
  • the slope 112 d is a portion guiding the clutch oil flowing out of the tip portion 121 of the shaft 120 toward the center fitting portion 112 a , and expands diametrically outward such that the slope 112 d descends from the portion to which the release bearing 112 c is fitted, toward the center fitting portion 112 a .
  • the angle of the slope 112 d is set appropriately in accordance with the amount of the clutch oil to be guided toward the center fitting portion 112 a .
  • the angle of the slope 112 d is preferably about 1 degrees or larger and about 5 degrees or smaller, for example.
  • the slope 112 d is formed at the entirety of a region between the portion to which the release bearing 112 c is fitted and the center fitting portion 112 a .
  • the center fitting portion 112 a and the oil receiver 112 b include oil path expansion portions 112 e formed therein.
  • the oil path expansion portions 112 e are provided in the center cylindrical portion 111 a so as to expand diametrically outward.
  • the oil path expansion portions 112 e expand diametrically outward in a portion in the circumferential direction in which the center fitting portion 112 a is formed.
  • the oil path expansion portions 112 e are each an example of a recessed portion.
  • the oil path expansion portions 112 e are each a portion actively causing the clutch oil present in the oil receiver 112 b to the outside of the oil receiver 112 b , and are each formed to have a groove-like shape protruding diametrically outward from inner circumferential surfaces of the center fitting portion 112 a and the oil receiver 112 b .
  • three oil path expansion portions 112 e are formed at an equal interval along a circumferential direction of the oil receiver 112 b . As shown in FIG.
  • the oil path expansion portions 112 e are each located between two presser-side cam portions 111 d adjacent to each other in the circumferential direction. As shown in FIG. 9 , the oil path expansion portions 112 e are each located closer to a presser-side slipper cam surface 111 ds . With this configuration, the clutch oil flowing to the outside of the center cylindrical portion 111 a via the oil path expansion portions 112 e is effectively supplied also to the presser-side slipper cam surfaces 111 ds.
  • the three oil path expansion portions 112 e are formed in the entirety of a region in the center cylindrical portion 111 a from at least a central portion in an axial direction thereof to an end thereof on the clutch center 110 side.
  • the oil path expansion portions 112 e extend from an end, on the slope 112 d side, of the portion to which the release bearing 112 c is fitted, to a tip portion (left end in the figure) of the center fitting portion 112 a . That is, the oil path expansion portions 112 e are each formed like a groove extending continuously along the slope 112 d and the center fitting portion 112 a .
  • the oil path expansion portions 112 e expand diametrically outward so as to have a slope descending from the portion to which the release bearing 112 c is fitted, toward the center fitting portion 112 a.
  • a gap is formed between each of the oil path expansion portions 112 e and an outer circumferential portion of the driven shaft coupling portion 110 a .
  • the size of the gap is set appropriately in accordance with the amount of the clutch oil to be distributed.
  • the size of the gap is preferably at least 10 times the size tolerance between the inner diameter of the center fitting portion 112 a and the outer diameter of the driven shaft coupling portion 110 a , and more preferably at least 100 times the size tolerance, for example.
  • the oil path expansion portions 112 e each include an opening 112 f formed therein.
  • a sum of the groove widths of the three oil path expansion portions 112 e is at most a half of the length of the center cylindrical portion 111 a in the circumferential direction.
  • the openings 112 f are each a portion actively causing the clutch oil present in the oil receiver 112 b to the outside of the oil receiver 112 b .
  • the openings 112 f are each formed by a portion of the center portion cylindrical 111 a in the circumferential direction being partially cut off.
  • the openings 112 f are each formed by a portion of the corresponding oil path expansion portion 112 e being cut off.
  • each opening 112 f is located between two of the presser-side cam portions 111 d adjacent to each other in the circumferential direction.
  • the opening 112 f is located closer to the presser-side slipper cam surface 111 d .
  • the openings 112 f extend from the tip portion (left end in FIG. 1 ) of the center fitting portion 112 a to a position overlapping the oil receiver 112 b in the circumferential direction.
  • An end 112 x of each opening 112 f on the second direction D 2 side is located ahead, in the first direction D 1 , of an end 111 x of the corresponding presser-side slipper cam surface 111 ds on the second direction D 2 side.
  • the ring-shaped intermediate portion 111 b is a flange-shaped portion formed between the center cylindrical portion 111 a and the plate sub holder 111 e .
  • the ring-shaped intermediate portion 111 b includes three cylindrical housings 111 c along the circumferential direction.
  • the cylindrical housings 111 c are each formed in the corresponding presser-side cam portion 111 d having the Assist & Slipper (registered trademark) mechanism described above.
  • the three cylindrical housings 111 c are portions respectively housing clutch springs 114 described below, and are circular. More specifically, the three cylindrical housings 111 c are recessed at an equal interval along a circumferential direction of the plate presser 111 .
  • the clutch springs 114 are respectively housed in the recessed cylindrical housings 111 c .
  • the above-described three cylindrical supports 110 c are located between the three cylindrical housings 111 c in the circumferential direction in a state where the cylindrical supports 110 c run through the plate presser 111 .
  • the presser-side cam portions 111 d are each formed to have a trapezoidal shape having a cam surface formed of a slope acting as an Assist & Slipper (registered trademark) mechanism.
  • the Assist & Slipper mechanism slides on the corresponding center-side cam portion 110 d to generate an assist torque or a slipper torque.
  • the plate presser 111 includes three presser-side cam portions 111 d .
  • the number of the presser-side cam portions 111 d is not limited to three.
  • the presser-side cam portions 111 d are located diametrically outward of the center cylindrical portion 111 a .
  • the presser-side cam portions 111 d are located at an equal interval along the circumferential direction of the plate presser 111 .
  • the presser-side cam portions 111 d each include a presser-side assist cam surface 111 da and a presser-side slipper cam surface 111 ds .
  • the presser-side assist cam surfaces 111 da are each contactable with the corresponding center-side assist cam surface 110 da .
  • the presser-side assist cam surfaces 111 da are each configured to generate a force in such a direction as to cause the plate presser 111 to approach the clutch center 110 , in order to increase a pressing force (contact pressure force) between the input-side rotating plates 105 and the output-side rotating plates 106 , when the plate presser 111 rotates with respect to the clutch center 110 .
  • the presser-side slipper cam surfaces 111 ds are each contactable with the corresponding center-side slipper cam surface 110 ds .
  • the presser-side slipper cam surfaces 111 ds are each configured to separate the plate presser 111 from the clutch center 110 , in order to decrease the pressing force (contact pressure force) between the input-side rotating plates 105 and the output-side rotating plates 106 , when the plate presser 111 rotates with respect to the clutch center 110 .
  • the presser-side assist cam surface 111 da of one presser-side cam portion 111 d and the presser-side slipper cam surface 111 ds of the other presser-side cam portion 111 d are opposed to each other in the circumferential direction.
  • the plate sub holder 111 e is a portion holding another portion of the plurality of output-side rotating plates 106 together with the input-side rotating plates 105 , and has a cylindrical shape extending in an axial direction of the plate presser 111 in an outer edge of the plate presser 111 .
  • the plate sub holder 111 e includes an outer circumferential portion formed of an external gear-shaped spline, and holds the output-side rotating plates 106 and the input-side rotating plates 105 located alternately in a state where the output-side rotating plates 106 and the input-side rotating plates 105 are displaceable in the axial direction of the plate presser 111 and are rotatable integrally with the plate presser 111 .
  • the plate sub holder 111 e includes a plate pressing portion 111 f formed in a tip portion thereof.
  • the plate pressing portion 111 f is a portion pressing the output-side rotating plates 106 and the input-side rotating plates 105 held by the plate sub holder 111 e toward the plate receiver 110 f to put the output-side rotating plates 106 and the input-side rotating plates 105 into close contact with each other.
  • the plate pressing portion 111 f is formed of a base portion, of the cylindrical plate sub holder 111 e , protruding like a flange diametrically outward.
  • the plate presser 111 is attached to the clutch center 110 by three attachment bolts 113 .
  • the clutch springs 114 are respectively housed in the three cylindrical housings 111 c , and the cylindrical supports 110 c run through the plate presser 111 between the three cylindrical housings 111 c in the circumferential direction.
  • the attachment bolts 113 are tightened to the cylindrical supports 110 c via stopper members 115 .
  • the plate presser 111 is secured to the clutch center 110 .
  • the shaft 120 is a component transferring a rotation driving force of the clutch center 110 to a driven body (not shown) such as a wheel or the like, and is formed of a steel material shaped into a hollow cylinder.
  • the tip portion 121 at one end (right end in the figure) of the shaft 120 supports the input rotating body 103 via the needle bearing 104 such that the input rotating body 103 is rotatable, and the clutch center 110 is spline-fitted to the shaft 120 .
  • a nut 122 is fitted, by a screw, to the tip portion at the right end (in the figure) of the shaft 120 to prevent the clutch center 110 from being pulled off from the shaft 120 .
  • the hollow portion 123 acts as a flow path of the clutch oil to be supplied into the clutch device 100 , and is provided with the push rod 124 .
  • the clutch oil flows in the shaft 120 , that is, the hollow portion 123 .
  • One end (left end in the figure) of the push rod 124 of the shaft 120 is coupled with a clutch release mechanism (not shown), and the other end (right end in the figure) of the push rod 124 presses a push member 125 .
  • the push rod 124 is formed to have a diameter shorter than an inner diameter of the hollow portion 123 , and thus the flowability of the clutch oil in the hollow portion 123 is guaranteed.
  • the clutch device 100 operates as follows.
  • the clutch release mechanism presses the push member 125 , and thus, the plate presser 111 is displaced in a direction away from the clutch center 110 against an elastic force of the clutch springs 114 .
  • the clutch center 110 enters a clutch-OFF state, in which the friction coupling between the input-side rotating plates 105 and the output-side rotating plates 106 is canceled, and thus, rotational driving attenuates or stops. That is, the rotation driving force of the prime mover is blocked and is not transferred to the clutch center 110 .
  • the clutch oil flowing out of the tip portion 121 of the shaft 120 is actively guided toward the center fitting portion 112 a via the slope 112 d , in the same manner as in the clutch-ON state.
  • the plate presser 111 is separated from the clutch center 110 , and thus, the amount of fitting between the center fitting portion 112 a and the driven shaft coupling portion 110 a decreases.
  • This enlarges areas, of the oil path expansion portions 112 e and the openings 112 f , that are exposed in the center cylindrical portion 111 a .
  • the clutch oil in the oil receiver 112 b more actively flows to the outside of the center cylindrical portion 111 a and is distributed to various portions in the clutch device 100 .
  • the clutch oil may be actively guided to the gaps between the input-side rotating plates 105 and the output-side rotating plates 106 separated from each other.
  • the plate presser 111 is released from the state of being pressed by the clutch release mechanism (not shown) through the push member 125 , and thus, the plate presser 111 is displaced in a direction toward the clutch center 110 by an elastic force of the clutch springs 114 .
  • the center cylindrical portion 112 a of the plate presser 111 is slidably fitted to the outer surface of the driven shaft coupling portion 110 a of the clutch center 110 , and the slope 112 d expanding diametrically outward toward the center fitting portion 112 a is formed at the inner circumferential surface of the oil receiver 112 b of the plate presser 111 , throughout the circumferential direction thereof.
  • the slope 112 d is formed at a region between the portion, of the oil receiver 112 b , to which the release bearing 112 c is fitted and the center fitting portion 112 a , throughout the circumferential direction.
  • the slope 112 d is formed at least at a portion of the inner circumferential surface of the oil bearing portion 112 b , more specifically, at a slope having an inner diameter expanding toward the center fitting portion 112 a .
  • one slope 112 d may be formed in the circumferential direction of the oil receiver 112 b and in the axial direction.
  • the slopes 112 d may be formed intermittently in the circumferential direction of the oil receiver 112 b or in the axial direction.
  • the center cylindrical portion 111 a includes the oil path expansion portions 112 e in a portion of the center fitting portion 112 a and the oil receiver 112 b .
  • the center fitting portion 111 a may effectively guide the clutch oil therein to the outside thereof.
  • the oil path expansion portions 112 e may be omitted to form the center fitting portion 111 a .
  • the oil path expansion portions 112 e and the openings 112 f are omitted from the center fitting portion 112 a .
  • the oil path expansion portions 112 e may be formed in the entirety of, or a portion of, the oil receiver 112 b in the axial direction of the center cylindrical portion 111 a as long as the oil path expansion portions 112 e are connected with the center fitting portion 112 a .
  • the oil path expansion portions 112 e do not need to be connected with the oil receiver 112 b .
  • the ease of discharging the clutch oil may be improved in the case where the oil path expansion portions 112 e are connected with the oil receiver 112 b.
  • the center cylindrical portion 111 a includes the openings 112 f in a portion of the center fitting portion 112 a and the oil receiver 112 b .
  • the center cylindrical portion 111 a may effectively guide the clutch oil therein to the outside thereof.
  • the openings 112 f may be omitted to form the center cylindrical portion 111 a .
  • the plate presser 111 shown in FIG. 6 only the openings 112 f are omitted from the center fitting portion 112 a.
  • the center cylindrical portion 111 a may include the openings 112 f formed in one of the center fitting portion 112 a and the oil receiver 112 b .
  • the openings 112 f may be formed in the entirety of, or a portion of, the center cylindrical portion 111 a in the axial direction.
  • the openings 112 f do not need to be connected with the oil receiver 112 b .
  • the ease of discharging the clutch oil may be improved in the case where the openings 112 f are connected with the oil receiver 112 b.
  • the openings 112 f are formed at positions facing a central portion of the plate holder 110 e in an axial direction thereof.
  • the clutch oil in the center cylindrical portion 111 a is supplied, via the openings 112 f , to the outside of the center cylindrical portion 111 a , more specifically, a central portion, of the plate holder 110 e , where the input-side rotating plates 105 and the output-side rotating plates 106 are aligned.
  • the clutch oil may effectively lubricate the entirety of the input-side rotating plates 105 and the output-side rotating plates 106 .
  • the openings 112 f may be formed at positions facing a non-central position (position shifted from the central position) of the plate holder 110 e in the axial direction thereof.
  • the center fitting portion 112 a is formed to expand, in a stepped manner (represented by dashed circle D in FIG. 1 ), at a border with the oil receiver 112 b and then to be cylindrical.
  • the center cylindrical portion 111 a may form a clutch oil reservoir at the stepped border between the center fitting portion 112 a and the oil receiver 112 b , and thus may easily guide the clutch oil to a region between the driven shaft coupling portion 110 a and the center fitting portion 112 a .
  • the center fitting portion 112 a may be formed to be cylindrical without the stepped portion being formed at the border with the oil receiver 112 b.
  • the oil path expansion portions 112 e are formed closer to the presser-side slipper cam surfaces 111 ds .
  • the oil path expansion portions 112 e are not limited to this.
  • the oil path expansion portions 112 e may be located closer to the presser-side assist cam surfaces 111 da .
  • the oil path expansion portions 112 e may be provided at a middle position between the presser-side slipper cam surfaces 111 ds and the presser-side assist cam surfaces 111 da in the circumferential direction.
  • the openings 112 f are located closer to the presser-side slipper cam surfaces 111 ds .
  • the openings 112 f are not limited to this.
  • the openings 112 f may be located closer to the presser-side assist cam surfaces 111 da .
  • the openings 112 f may be provided at a middle position between the presser-side slipper cam surfaces 111 ds and the presser-side assist cam surfaces 111 da in the circumferential direction.
  • the end 112 x of each opening 112 f on the second direction D 2 side is located ahead, in the first direction D 1 , of the end 111 x of the corresponding presser-side slipper cam surface 111 ds on the second direction D 2 side.
  • the end 112 x is not limited to this.
  • the end 112 x of each opening 112 f on the second direction D 2 side may be ahead, in the second direction D 2 , of the end 111 x of the corresponding presser-side slipper cam surface 111 ds on the second direction D 2 side.
  • each opening 112 f each have a constant width in a circumferential direction thereof.
  • the openings 112 f are not limited to this.
  • each opening 112 f may include a first portion 112 fa having a first length L 1 in the circumferential direction and a second portion 112 fb located ahead of the first portion 112 fa in the second direction D 2 and having a second length L 2 , shorter than the first length L 1 , in the circumferential direction.
  • the openings 112 f are each formed by a portion, of the center cylindrical portion 111 a , that is between the presser-side cam portions 111 d adjacent to each other in the circumferential direction being partially cut off.
  • the openings 112 f are not limited to this.
  • the openings 112 f may each be formed by a portion, of the center cylindrical portion 111 a , that is between the presser-side cam portions 111 d adjacent to each other in the circumferential direction being entirely cut off. That is, as shown in FIG.
  • the openings 112 f may each be formed from an end 111 dx of the presser-side assist cam surface 111 da on the first circumferential direction S 1 side to an end 111 dy of the presser-side slipper cam surface 111 ds on the second circumferential direction S 2 side.
  • the center fitting portion 112 a is slidably fitted to the outer surface of the driven shaft coupling portion 110 a directly.
  • the center fitting portion 112 a may be fitted to the outer surface of the driven shaft coupling portion 110 a indirectly with another member such as a sleeve or the like being located between the center fitting portion 112 a and the driven shaft coupling portion 110 a.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
US18/700,071 2021-10-14 2022-10-03 Clutch device and motorcycle Active US12473951B2 (en)

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JP2021-168978 2021-10-14
JP2021168978 2021-10-14
JP2022-108653 2022-07-05
JP2022108653 2022-07-05
PCT/JP2022/037003 WO2023063153A1 (ja) 2021-10-14 2022-10-03 クラッチ装置および自動二輪車

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JP7842319B1 (ja) * 2024-12-27 2026-04-07 株式会社エフ・シー・シー クラッチ装置

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4331768Y1 (https=) 1964-12-21 1968-12-24
JPS5628321A (en) 1979-08-13 1981-03-19 Yamaha Motor Co Ltd Wet type multiple disc clutch
US20090071792A1 (en) * 2007-09-12 2009-03-19 Kabushiki Kaisha F.C.C. Power transmitting apparatus
US20100163361A1 (en) 2008-12-25 2010-07-01 Masayoshi Suzuta Multiple disc clutch apparatus
US20110073429A1 (en) * 2009-09-30 2011-03-31 Honda Motor Co., Ltd. Multi-plate clutch system
JP2013104544A (ja) 2011-11-17 2013-05-30 F C C:Kk クラッチ装置
US9689439B2 (en) * 2015-02-09 2017-06-27 Honda Motor Co., Ltd. Clutch device having a back torque limiter
US20180180113A1 (en) * 2016-12-28 2018-06-28 Honda Motor Co., Ltd. Oil supply structure of clutch device
EP3366939A1 (en) 2017-02-27 2018-08-29 Yamaha Hatsudoki Kabushiki Kaisha Motorcycle
US20190027369A1 (en) * 2017-07-21 2019-01-24 Shin-Etsu Chemical Co., Ltd. Composition for forming organic film, patterning process, and resin for forming organic film
JP2019078373A (ja) 2017-10-26 2019-05-23 株式会社エフ・シー・シー クラッチ装置
US20190257369A1 (en) 2018-02-19 2019-08-22 Honda Motor Co., Ltd. Pressure plate and clutch device
US20190285123A1 (en) * 2018-03-14 2019-09-19 Exedy Corporation Clutch device
CN111255815A (zh) 2020-01-17 2020-06-09 重庆隆鑫机车有限公司 强化离合器及发动机

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6725569B2 (ja) * 2018-03-14 2020-07-22 株式会社エクセディ クラッチ装置

Patent Citations (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4331768Y1 (https=) 1964-12-21 1968-12-24
JPS5628321A (en) 1979-08-13 1981-03-19 Yamaha Motor Co Ltd Wet type multiple disc clutch
US20090071792A1 (en) * 2007-09-12 2009-03-19 Kabushiki Kaisha F.C.C. Power transmitting apparatus
JP2009068578A (ja) 2007-09-12 2009-04-02 F C C:Kk 動力伝達装置
US20100163361A1 (en) 2008-12-25 2010-07-01 Masayoshi Suzuta Multiple disc clutch apparatus
JP2010151232A (ja) 2008-12-25 2010-07-08 Honda Motor Co Ltd 多板式クラッチ装置
US20110073429A1 (en) * 2009-09-30 2011-03-31 Honda Motor Co., Ltd. Multi-plate clutch system
JP2013104544A (ja) 2011-11-17 2013-05-30 F C C:Kk クラッチ装置
US20150041275A1 (en) 2011-11-17 2015-02-12 Kabushiki Kaisha F.C.C. Clutch Device
US9689439B2 (en) * 2015-02-09 2017-06-27 Honda Motor Co., Ltd. Clutch device having a back torque limiter
US20180180113A1 (en) * 2016-12-28 2018-06-28 Honda Motor Co., Ltd. Oil supply structure of clutch device
JP2018105480A (ja) 2016-12-28 2018-07-05 本田技研工業株式会社 クラッチ装置の給油構造
EP3366939A1 (en) 2017-02-27 2018-08-29 Yamaha Hatsudoki Kabushiki Kaisha Motorcycle
JP2018141480A (ja) 2017-02-27 2018-09-13 ヤマハ発動機株式会社 モータサイクル
US20190027369A1 (en) * 2017-07-21 2019-01-24 Shin-Etsu Chemical Co., Ltd. Composition for forming organic film, patterning process, and resin for forming organic film
JP2019078373A (ja) 2017-10-26 2019-05-23 株式会社エフ・シー・シー クラッチ装置
US20200292010A1 (en) 2017-10-26 2020-09-17 Kabushiki Kaisha F.C.C. Clutch device
US20190257369A1 (en) 2018-02-19 2019-08-22 Honda Motor Co., Ltd. Pressure plate and clutch device
US20190285123A1 (en) * 2018-03-14 2019-09-19 Exedy Corporation Clutch device
CN111255815A (zh) 2020-01-17 2020-06-09 重庆隆鑫机车有限公司 强化离合器及发动机

Non-Patent Citations (6)

* Cited by examiner, † Cited by third party
Title
Official Communication issued in corresponding European Patent Application No. 25166745.7, mailed on May 9, 2025, 9 pages.
Official Communication issued in corresponding Japanese Patent Application No. 2022-162731, mailed on Jul. 30, 2024, 3 pages.
Official Communication issued in International Patent Application No. PCT/JP2022/037003, mailed on Dec. 6, 2022.
Official Communication issued in corresponding European Patent Application No. 25166745.7, mailed on May 9, 2025, 9 pages.
Official Communication issued in corresponding Japanese Patent Application No. 2022-162731, mailed on Jul. 30, 2024, 3 pages.
Official Communication issued in International Patent Application No. PCT/JP2022/037003, mailed on Dec. 6, 2022.

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JP2023059248A (ja) 2023-04-26
EP4553331A3 (en) 2025-06-11
WO2023063153A1 (ja) 2023-04-20
EP4553331A2 (en) 2025-05-14
JP7707137B2 (ja) 2025-07-14
EP4417830A4 (en) 2024-10-30
JP2025085834A (ja) 2025-06-05
US20250237274A1 (en) 2025-07-24
EP4417830A1 (en) 2024-08-21
EP4417830B1 (en) 2026-01-21

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